EP1434023A2 - Sécheur à froid - Google Patents

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Publication number
EP1434023A2
EP1434023A2 EP03028831A EP03028831A EP1434023A2 EP 1434023 A2 EP1434023 A2 EP 1434023A2 EP 03028831 A EP03028831 A EP 03028831A EP 03028831 A EP03028831 A EP 03028831A EP 1434023 A2 EP1434023 A2 EP 1434023A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
guide channels
heat
profile
section
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP03028831A
Other languages
German (de)
English (en)
Other versions
EP1434023A3 (fr
EP1434023B1 (fr
Inventor
Michael Feisthauer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kaeser Kompressoren GmbH
Original Assignee
Kaeser Kompressoren GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kaeser Kompressoren GmbH filed Critical Kaeser Kompressoren GmbH
Publication of EP1434023A2 publication Critical patent/EP1434023A2/fr
Publication of EP1434023A3 publication Critical patent/EP1434023A3/fr
Application granted granted Critical
Publication of EP1434023B1 publication Critical patent/EP1434023B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26—Drying gases or vapours
    • B01D53/265—Drying gases or vapours by refrigeration (condensation)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0038—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for drying or dehumidifying gases or vapours

Definitions

  • the invention relates to a refrigeration dryer, in particular a compressed air refrigeration dryer for drying a gaseous working fluid while cooling of the gaseous working fluid by using a refrigerant fluid according to the Features of the preamble of claim 1 and a heat exchanger element according to the preamble of patent claim 26 or 27.
  • the working fluid For refrigeration dryers, especially compressed air refrigeration dryers for drying a gaseous working fluid while cooling the gaseous working fluid by using a cooling fluid, the working fluid first passes through one Pre-heat exchanger section and then a main heat exchanger section. In the pre-heat exchanger section, the on cools down the working fluid through the dried and cooled Working fluid in the counterflow principle. In the main heat exchanger section the working fluid is further cooled by a cooling fluid, so that Moisture is condensed out of the working fluid and removed can.
  • a refrigeration dryer according to the prior art is for example in DE 100 30 627 A1.
  • the present invention has for its object a refrigeration dryer specify that has an improved structure, especially in a compact Design ensures effective heat exchange. simultaneously heat exchanger elements are to be specified that such a achieve effective heat exchange.
  • a key concept of the present invention is that all flow channels the pre-heat exchanger section and / or the main heat exchanger section essentially by hollow chamber profiles with a plurality of heat guide channels and / or of cold guide channels are, wherein the at least one heat exchanger element of the pre-heat exchanger section and / or the main heat exchanger section at the end is held and connected in a fluid-tight manner in one connection profile, the heat exchanger element being preferably an elongated tubular profile is formed and the heat guide channels and cold guide channels extend along the tube profile and wherein the heat guide channels and the cooling ducts formed integrally with the tubular profile Partitions are separated from each other.
  • the proposed structure allows a particularly compact Design, especially when two or more heat exchanger elements at the end held or connected in a joint connection profile in a fluid-tight manner are.
  • This advantage already exists when two or more heat exchanger elements of the pre-heat exchanger section or Main heat exchanger section at the ends in a common connection profile are held and connected in a fluid-tight manner.
  • the heat guide channels and the cold guide channels are designed adjacent to each other, but arranged alternately.
  • the heat guide channels are and / or the cooling ducts transverse to the longitudinal extent of the tubular profile is opened at the end through openings in such a way that Outflow to the heat guide channels and / or cold guide channels transversely to the longitudinal extent of the tubular profile.
  • this configuration is a simple and convenient way of connecting the heat guide ducts and / or the cooling ducts can be realized.
  • all heat exchanger elements are the pre-heat exchanger section and the main heat exchanger section held fluid-tight at one end in one or two common connection profiles and connected.
  • connection profile is also expediently essentially a hollow chamber profile educated.
  • the arrangement is made Pre-heat exchanger section, from main heat exchanger section as well at the end of each connection profiles provided from a total of at least four hollow chamber profiles formed.
  • a modular structure of the overall order is therefore envisaged.
  • This modular structure or the formation of pre-or main heat exchanger section offers the possibility of simple capacity adjustment through Length and / or number of exchanger tubes.
  • the connection of the individual components can be done without complex connection procedures.
  • the at least four hollow profiles are located in the form of only two different types, which can be found in the Differentiate profile cross-sections. This allows the modular structure can be simplified because only two different types of profile cross-sections must be provided.
  • connection profile integrally formed, which further reduces the manufacturing costs while minimizing connection and tightness problems.
  • connection profile comprises at least one, preferably at least two fluid guide chambers through the Hollow chamber profile of the connection profile are defined.
  • the connection profile itself to guide the fluid, namely the Working fluids and / or the refrigerant fluid are used, but not at all is imperative. Rather, separate fluid guides, in particular in the case of the refrigerant, conceivable for the main heat exchanger section.
  • connection profile is as Extruded profile, in particular designed as an extruded aluminum profile. This type of training allows an inexpensive and reproducible Production.
  • connection profiles are at both ends of the heat exchanger elements appropriate connection profiles provided. These connection profiles can according to a further advantageous aspect of the present invention be clamped together via rigid bracing elements.
  • the bracing elements are in a concrete, simple but advantageous embodiment formed as rods.
  • the rods be guided at least partially through the heat exchanger elements. This results in a particularly useful bracing, since relative is evenly acted on the heat exchanger elements.
  • connection profiles made of the same basic material as the heat exchanger elements educated. This also reduces manufacturing costs and eliminates them Material adjustment problems. In the case of metal as the material used there is also no potential for voltage, which is the case when using different Materials could cause problems. Particularly preferred is training in aluminum.
  • the tube profile as one-piece profile, preferably designed as an extruded aluminum profile.
  • Aluminum is suitable for both gaseous and above all even with liquid fluids a preferred material that can also be used easy to edit.
  • the heat exchanger element is designed as a one-piece profile.
  • the openings of the heat guide channels and / or the openings of the Cold guide channels at the end of the tubular profile essentially in one plane lie.
  • the openings of a Arrange group of channels essentially in one plane can be provided on the one hand.
  • the openings of the second type of channels can also be provided be arranged on a (different) level.
  • the openings are particularly preferred provide both types of channels in one plane, being in this Embodiment, for example, the openings of a type of channels on a Inside of the tubular profile and the openings of the other type of channels can be provided on an outside of the tubular profile.
  • profiles in particular ribs.
  • Such ribs or profiles increase the heat transfer flow and can be designed as an extruded profile without the tube profile greater manufacturing effort are also trained.
  • the heat guide channels are and the cooling ducts around one along the heat exchanger element trending central channel arranged around.
  • the central channel is in fluid connection at the end via openings with the heat guide channels or the cold guide channels and is closed towards the center of the tubular profile by means of a sealing element.
  • the sealing element is intended to have the effect that the fluid must also flow from the central channel through the heat guide channels or cold guide channels provided and cannot pass through the central channel from one end of the heat exchanger element to the other end of the heat exchanger element.
  • the heat exchanger element at least two heat management channels and cooling ducts.
  • the division of the tube profile into one A large number of segments seems to make sense, as this means the wall surfaces and thus the overall heat transfer rate can be increased.
  • the heat conduction channels and / or the cooling ducts perpendicular to their longitudinal extension, have a substantially circular segment-shaped cross section.
  • the partitions between the heat conduction channels and / or cooling ducts but also to enlarge the heat exchanger area have a curved or kinked course.
  • the partitions can have a cross section for the longitudinal extension of the heat exchanger element a spiral arm Show course.
  • the profile can be helically rotated in the axial direction be d.
  • the heat guide channels or cold guide channels wind like a screw around a central axis.
  • heat exchanger element for liquid or gaseous media proposed that in particular in a refrigeration dryer according to the invention can be used.
  • the heat exchanger element described here is however in no way limited to the application "refrigeration dryer” but can also be used in any other conceivable application Find.
  • the heat exchanger element is present invention as a preferably elongated tubular profile formed and comprises several extending along the tubular profile Heat management channels and cold management channels.
  • the heating and cooling ducts are adjacent to each other but arranged alternately, the heat guide channels and the cold guide channels through integral Partitions formed with the tubular profile are separated from each other.
  • the outer walls opposite the heat guide channels or the cold guide channels the outer walls of the cooling ducts or the heat ducts protruding at least on an outside or inside in cross section are trained.
  • this enables simple and reproducible training of openings on the above heat guide channels or cold guide channels.
  • This can be done according to a preferred aspect of the invention by material removal, with a circular configuration of the cross-section of the tubular profile, turning off the openings in certain areas can be made.
  • material removal with a circular configuration of the cross-section of the tubular profile, turning off the openings in certain areas can be made.
  • such a material could be removed from a substantially flat basic shape can also be caused by milling or grinding. openings can of course also be created by drilling holes, etc.
  • a heat exchanger element which is preferably an elongated Tube profile is formed and several along the tube profile extending heat guide channels and cold guide channels, wherein the heat guide channels and the cold guide channels are adjacent to one another, but are arranged alternately, the heat guide channels and the cooling ducts by integrally formed with the tubular profile Partitions are separated from each other, the heat guide channels and the Cold-guiding ducts at the end at right angles to the longitudinal extent of the tubular profile be opened through openings such that inflow or outflow to the Heat guide channels and cold guide channels transverse to the longitudinal extension of the tubular profile takes place, furthermore openings of the heat guide channels with respect to the openings of the cooling ducts in a longitudinal extension of the tubular profile are arranged offset. Also in this configuration is a convenient way of connecting the heat exchanger element given.
  • Fig. 1 shows the basic structure of a refrigeration dryer known per se.
  • the refrigeration dryer comprises a pre-heat exchanger section 11 and one Main heat exchanger section 12 and a condensate separator 40 and a refrigerant fluid circuit 42.
  • the gaseous working fluid is initially via a working fluid inlet 38 led into the pre-heat exchanger section 11.
  • the pre-cooled working fluid then enters the main heat exchanger section 12, in which it is cooled even further, preferably below the dew point of the carried moisture, so that the moisture in the working fluid at least partially condensed out.
  • the condensate will come out separated from the main heat exchanger section 12 on the condensate separator 40 and supplied to the condensate drain 41.
  • the chilled and dried Working fluid enters the pre-heat exchanger section 11, where it is called Cold fluid is used for the uncooled and moist working fluid.
  • the cooled and dried working fluid is again at a predetermined desired output temperature warms up and then leaves the refrigeration dryer via a working fluid outlet 39.
  • both a liquid and a gaseous refrigerant fluid can be used.
  • the cooling fluid is over a Cold fluid inlet 43 led into the main heat exchanger section 12 where it the pre-cooled working fluid cools and warms up at the same time.
  • the refrigerant fluid is fed into the refrigerant fluid circuit 42.
  • Fig. 2 shows an expedient embodiment of the pre-heat exchanger section 11 and the main heat exchanger section 12 of a refrigeration dryer according to the invention, which can be constructed in the rest of FIG. 1.
  • the - in the present case elongated - heat exchanger elements 13, 14 the pre-heat exchanger section 11 and the main heat exchanger section 12 are fluid-tight at both ends in a connection profile 15, 16, 52, 53 held and connected.
  • the heat exchanger elements 13, 14 is elongated in the exemplary embodiments shown here are, it is also conceivable to spiral the entire heat exchanger tube wind. The advantage of this is that there is a smaller one Space for the heat exchanger tube results. Its functionality remains essentially unaffected by the spiral winding.
  • connection profiles 15, 16, 52, 53 are at the ends the heat exchanger elements 13, 14 of the pre-heat exchanger section 11 and the main heat exchanger section 12 located connection profiles 15, 16, 52, 53 parallel and in pairs adjacent to each other in their longitudinal extent arranged.
  • the connection profiles 15, 16, 52, 53 are on the flattened adjacent side.
  • the connection profiles 16 and 53 or 15 and 52 can then also be connected to one another, for example by screwing. Openings (not shown in Fig. 2) in the adjacent Side of the connection profiles 15 and 52 or 16 and 53, for example generated by drilling can then allow the working fluid from the pre-heat exchanger section 11 to the main heat exchanger section 12 arrives and vice versa.
  • connection profiles 15, 16, 52, 53 are at both ends with end plates 54 locked.
  • the end plates 54 are connected to the connection profiles 15, 16, 52, 53 screwed and sealed with a seal (not shown in Fig. 2).
  • the connection profiles 15, 16, 52, 53 are with rigid bracing elements 19, 20 in the form of rods guided through the heat exchanger elements tense together.
  • connection profiles 15, 16 of the pre-heat exchanger section 11 the supply and discharge of the uncooled or pre-cooled and the dried Working fluids to and from the heat exchanger elements 13 and the distribution of the uncooled and the dried working fluid to the Heat exchanger elements 13.
  • connection profiles 52, 53 of the main heat exchanger section 12 the supply and discharge of the pre-cooled or the cooled working fluid to or from the heat exchanger elements 14 and the distribution of the pre-cooled working fluid on the heat exchanger elements 14.
  • the cooling fluid can also via the connection profiles 52, 53 to or from the heat exchanger elements 14 are supplied or discharged.
  • the refrigerant fluid becomes direct via the refrigerant fluid inlet 43 led to the heat exchanger elements 14 and leaves them directly via the cold fluid outlet 44.
  • cold fluid inlet 43 and cold fluid outlet 44 can, for example, be orthogonal to the longitudinal axis of the connection profiles 52, 53 extending channel can be formed, the cooling fluid through the connection profiles 52, 53 leads to the heat exchanger elements 14.
  • the working fluid exits at the working fluid inlet 38 at a temperature of for example, 35 ° C in the pre-heat exchanger section 11 and is about the connection profile 16 to the parallel in the present embodiment arranged and switched heat exchanger elements 13 out. There it becomes countercurrent to the already cooled and dried working fluid passed and cooled. The already cooled and dried working fluid heats up from 4 ° C to 27 ° C and leaves the pre-heat exchanger section 11 via the connection profile 16 and the working fluid outlet 39. The pre-cooled working fluid from the pre-heat exchanger section 11 is now in the connection profile 52 via the connection profile 15 guided and from there to both the connection technology and geometry heat exchanger elements 14 of the main heat exchanger section arranged in parallel 12 distributed.
  • the heat exchanger elements 14 that precooled working fluid in direct current bypasses the cooling fluid, the reaches the heat exchanger elements 14 via the cold fluid inlet 43.
  • the Pre-cooled working fluid is changed to 3 in the main heat exchanger section 12 ° C cooled, the moisture carried condensed to a large extent. Chilled working fluid and condensate leave the main heat exchanger section 12 via the connection profile 53 to the condensate separator 40.
  • the chilled and dried working fluid which is a temperature of 4 ° C, is then on the connection profile 15 on the Heat exchanger elements 13 of the pre-heat exchanger section 11 out.
  • the Refrigerant fluid leaves the main heat exchanger section 12 via the refrigerant fluid outlet 44th
  • connection profile of the refrigeration dryer in perspective view.
  • the connection profile is made in one piece and comprises two fluid guide chambers 17, 18 for guiding the working fluid and possibly also the refrigerant fluid.
  • connection profile faces the heat exchanger elements 13, 14 Side several openings 45 for inserting or performing Heat exchanger elements 13, 14 and an opening 46 for connecting one Fluid line (not shown in Fig. 3). Threaded holes 55 on the front side of the connection profile serve the connection profile with the end plate 54 to screw and thus seal to the outside. In the end plate 54 bores 56 are provided for this purpose.
  • the fluid guide chambers 17, 18 are separated from one another by an intermediate wall 47 separated, which has openings 48 into which the heat exchanger elements 13, 14 inserted or applied and through which the bracing elements 19, 20 can be carried out in the form of rods (Fig. 4).
  • Fig. 5 shows a perspective view of the heat exchanger elements 13, 14 opposite side of the connection profile according to Fig. 3.
  • the connection profile has a plurality of openings 49 for carrying out the bracing elements 19, 20 and a further opening 50 for connection a fluid line (not shown in Fig. 5).
  • the connection profile flattened on one or on the two closed long sides, so that there is a rectangular cross section, several can be such connection profiles very space-saving on the closed long side arrange adjacent to each other.
  • the fluid flow channels of each other Adjoining connection profiles can then be connected to each other through openings be connected (not shown in Fig. 5).
  • Fig. 6 shows a cross section of a heat exchanger element of the invention Cold dryer.
  • heat guide channels 21 and cold guiding channels 22 are adjacent and alternating arranged and separated from one another by partitions 27.
  • the alternating arranged heat guide channels 21 and cold guide channels 22 form a closed ring around a central axis, in the present Embodiment a central channel 29.
  • the closed Ring of heat guide channels 21 and cold guide channels 22 has one Outside 23 and an inside 24.
  • Embodiment For an improved heat transfer through an enlarged heat exchanger area are in the present Embodiment provide the cooling ducts 22 with ribs 28. For an enlarged heat exchanger surface, only the Heat guide channels 21 or both fluid channels with profiles or Ribs may be formed (not shown in Fig. 6).
  • the heat guide channels 21 protrude toward the inside 24 in cross section formed and the cold guide channels 22 are to the outside 23 formed in cross section above.
  • heat guide channels 21 have ends Openings 26 to the inside 24 of the heat exchanger element 13, 14 on.
  • the cold guide channels 22 have end openings 25 to the outside 23 of the heat exchanger element 13. It is also possible that the cold guide channels 22 to the inside 24 and the heat guide channels 21 are open to the outside 23 (not shown in FIG. 7) or that the openings of both channels face the same side, inside or outside lead, but in different planes transverse to the longitudinal extension of the Heat exchanger elements 13, 14 are arranged (not shown in FIG. 7).
  • the heat exchanger element 13 is in the refrigeration dryer on both sides in connection profiles 15, 16 held and connected (Fig. 8).
  • Fig. 9 shows the cross section a connection point of the connection profile 16 with the heat exchanger element 13 according to Fig. 8.
  • the heat exchanger element 13 is through the Opening 45 made in the connection profile 16 and applied to the opening 48.
  • the heat guide channels 21 and the cold guide channels 22 are on the end face of the heat exchanger element 13 against the fluid channel 17 a seal 30 sealed.
  • the central channel 29 stands with the heat guide channels 21 or the cold guide channels 22 in fluid communication and is towards the center of the tubular profile via an annular sealing element 34 closed with a sealing ring 35.
  • the fluid is forced by the central channel 29 through the heat conduction channels 21 or Cooling ducts 22 to flow.
  • a sealing ring 33 in the opening 45 of the connection profile 16 seals the fluid chamber 18 to the outside.
  • the Bracing element 19 leads through the annular sealing element 34, the central channel 29, opening 48, fluid chamber 17 and the opening 49, in which it is fastened with a clamping element 31.
  • Another sealing ring 32 on the clamping element 31 seals the fluid chamber 17 to the outside from.
  • Via the fluid channel 17 and the working fluid and possibly the refrigerant fluid can pass through the central channel 29 through the openings 26, 25 into the heat guide channels 21 or cold guide channels 22 enter or exit.
  • Figure 10 illustrates the junction of the connection profile 16 with the heat exchanger element 13 in a perspective view.
  • the supply and discharge of the working fluid and possibly the cooling fluid to or from the connection profile 16 takes place via fluid lines 36, 37 (FIG. 11).
  • the fluid line 36 is installed in the opening 46 of the fluid chamber 18.
  • the fluid line 37 is connected to the fluid chamber 17 via the opening 50 connected.
  • the openings 25, 26 of the heat guide channels 21 and the cold guide channels 22 also together on one side of the heat exchanger element 13 may be attached, for example on the outside 23 (FIG. 12).
  • the Openings 25 are then along the longitudinal axis of the heat exchanger element 13 arranged in a different plane than the openings 26 and become Example created by drilling holes.
  • the partitions 27 between the heat guide channels 21 and the cold guide channels 22 also have an inclined course (FIG. 13). This turns the Heat transfer available surface increases, so that improved heat exchange can take place. You can also use this Embodiment of the heat exchanger elements turbulence or turbulence generated in the airfoil, making it a very effective Heat transfer is achieved. Are the heat guide channels 21 and Cold guide channels 22 rotated helically in profile in the axial direction formed (not shown in Fig. 13), the swirls occur more intensely Form on, which also increases the efficiency of heat transfer can be increased again.
  • the heat exchanger elements can have an oval shape (Fig. 18), rectangular (Fig. 19) or triangular cross-section (Fig. 20), in which the heat guide channels 21 and cold guide channels 22 are arranged alternately side by side.
  • the different cross sections allow, for example, an optimal adaptation of the heat exchanger to different spaces.
  • very different flow profiles are generated, which makes the Have the heat exchanger adapted to a wide variety of requirements.
  • Heat guide channels 21 and cold guide channels 22 alternately in one closed ring arranged around a central axis a (Fig. 23), the one Has outside 23.
  • the supply of the working fluid and the cooling fluid can be from the front of the heat exchanger element or from the outside 23 take place.
  • the heat guide channels 21 and the cold guide channels 22 can be formed above in cross section. Openings 25, 26 can be in different planes transverse to the longitudinal extension of the Heat exchanger elements by grinding or milling as well as through bores be generated.
  • the rectangular heat guide channels 21 and cold guide channels 22 are alternately arranged in a rectangular profile. Because the heat management channels 22 and cold guide channels 22 in cross section up and down are formed above, can be ground by area or milling off the outer wall 51 or through holes 25, 26 be generated. Are the heat guide channels 21 and the cold guide channels 22 not formed above in cross section, the openings 25, 26 also by making holes in the outer wall 51 generate (Fig. 22).
  • FIG 24 shows another embodiment of a pre-heat exchanger section 11 and a main heat exchanger section 12 of a refrigeration dryer according to the Invention represents.
  • the heat exchanger elements 13, 14 of the pre-heat exchanger section 11 and the main heat exchanger section 12 are in the present Embodiment arranged in parallel in a row.
  • the heat exchanger elements 13, 14 are on one end in a common, one-piece Connection profile 52 held.
  • On the opposite side are the Heat exchanger elements 13 of the pre-heat exchanger section 11 in the end Connection profile 15 and the heat exchanger elements 14 of the main heat exchanger section 12 held at the end in the connection profile 16.
  • the connection profiles 15, 16, 52 are each provided with end plates 54 on the end faces locked.
  • connection profile 15 of the pre-heat exchanger section 11 Supply and discharge of the uncooled or dried working fluid or of the heat exchanger elements 13 and the distribution of the uncooled Working fluids on the heat exchanger elements 13.
  • connection profiles 16 of the main heat exchanger section 12 Via the connection profiles 16 of the main heat exchanger section 12 the removal of the cooled working fluid from the heat exchanger elements 14.
  • the refrigerant fluid is over the Cold fluid inlet 43 led directly to the heat exchanger elements 14 and leaves this directly via the cold fluid outlet 44.
  • cold fluid inlet 43 and Refrigerant fluid outlet 44 are orthogonal to the longitudinal axis of the connection profile 52 arranged and flowed through.
  • the working fluid enters the pre-heat exchanger section at the working fluid inlet 38 11 and is connected to the connection profile 15 in the present Embodiment arranged and connected heat exchanger elements in parallel 13 led. There it is countercurrently cooled and dried working fluid passed and cooled. The already cooled and dried working fluid heats up and leaves the pre-heat exchanger section 11 via the connection profile 15 and the working fluid outlet 39. The pre-cooled working fluid from the pre-heat exchanger section 11 is now in parallel via the common connection profile 52 arranged heat exchanger elements 14 of the main heat exchanger section 12 out. The precooled working fluid is in the heat exchanger elements 14 passed in direct current to the refrigerant fluid, which over the Cold fluid inlet 43 enters the heat exchanger elements 14.
  • the pre-chilled Working fluid is cooled in the main heat exchanger section 12 the moisture carried condenses to a large extent. Chilled working fluid and condensate leave the main heat exchanger section 12 via the connection profile 16 to the condensate separator 40 cooled and dried working fluid, is then over the connection profile 52 on the heat exchanger elements 13 arranged in parallel the pre-heat exchanger section 11 out.
  • the cooling fluid leaves the Main heat exchanger section 12 via the cold fluid outlet 44.
  • the advantage of this embodiment of the pre-heat exchanger section 11 and the main heat exchanger section 12 is the space-saving arrangement for very limited space, in case there are only a few connected in parallel Heat exchanger elements 13, 14 in the pre-heat exchanger section 11 and the main heat exchanger section 12 are needed.
  • the cold dryer according to the invention or the heat exchanger element according to the invention achieved according to the basic idea of the invention or in various preferred configurations in particular the following advantages.
  • a few, partly identical components can be used for various subtasks.
  • the individual components are connected using simple connection techniques also detachable possible.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • General Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Drying Of Solid Materials (AREA)
  • Inorganic Insulating Materials (AREA)
  • Treatments Of Macromolecular Shaped Articles (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Drying Of Gases (AREA)
EP03028831A 2002-12-24 2003-12-15 Sécheur à froid Expired - Lifetime EP1434023B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10261922A DE10261922A1 (de) 2002-12-24 2002-12-24 Kältetrockner
DE10261922 2002-12-24

Publications (3)

Publication Number Publication Date
EP1434023A2 true EP1434023A2 (fr) 2004-06-30
EP1434023A3 EP1434023A3 (fr) 2005-08-03
EP1434023B1 EP1434023B1 (fr) 2009-10-14

Family

ID=32404427

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03028831A Expired - Lifetime EP1434023B1 (fr) 2002-12-24 2003-12-15 Sécheur à froid

Country Status (4)

Country Link
US (1) US7040100B2 (fr)
EP (1) EP1434023B1 (fr)
AT (1) ATE445819T1 (fr)
DE (2) DE10261922A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2177255A1 (fr) 2008-10-15 2010-04-21 Kaeser Kompressoren GmbH Dispositif de séchage à froid

Families Citing this family (6)

* Cited by examiner, † Cited by third party
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US20040206095A1 (en) 2004-10-21
EP1434023A3 (fr) 2005-08-03
EP1434023B1 (fr) 2009-10-14
DE10261922A1 (de) 2004-07-15
ATE445819T1 (de) 2009-10-15
US7040100B2 (en) 2006-05-09
DE50312018D1 (de) 2009-11-26

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